Mining apparatus



Dec. 17, 1940. J, F, JOY

MINING. APPARATUS Filed March 9, 1937 9 Sheets-Sheet l Sam@ 4M/Imm.

Des. 17, 1940. 1 J. F. JOY

MINING APPARATUS 9 Sheets-Sheet 2 Filed March 9, 1937 Dec. 17, 1940. J. F. JOY 2,224,872

` MINING APPARATUS Filed March 9, 1937v 9 sheets-sheet s www.

fzFJay. I

Dec. 17, 1940.

J. F. JOY

MINING APPARATUS Filed March 9, `1925"? 9 Sheets-Sheet 4 lll IIIIIIIII n Dec. 17,1940. J. F. JOY 2,224,872

MINING APPARATUS Filed March 9, 1937 9 Sheets-Sheet 5 Dec. 17, 1940. J. F JOY MINING APPARATUS Filed March 9, 1937 9 Sheebs-SheetI 6- Dec. '17, 1940. J. F. .JOY 2,224,872

MINING APPARATUS Filed March 9, 1937 9 Sheets-Sheet 7 Dec. 17, 1940. F, JOY 2,224,872

MINING APPARATUS Filed March 9, 19,37 9 Sheets-Sheet 8 DEC. 17, 1940. F. JOY 2,224,872

MINING APPARATUS Filed March 9, 1957 9 Sheets-Sheet 9 Patented Dec. 17, 1940 UNITED s'ra'rizs'N IWINING APPARATUS Joseph F. Joy, Claremont, NQH., assignor to Sullivan Machinery Company, a. corporation of Massachusetts Application March 9, 1937, Serial No. 129,356

1 Claim.

'I'his invention relates to mining apparatus, and more particularly, but not exclusively, to improvements in a coal mining apparatus of the horizontal cutting, track cutter type adapted to operate while supported and guided by a mine trackway.

An object of this invention is to provide an improved coal mining apparatus of the type commonly known as a track cutter. Another object is` to provide an improved coal mining apparatus of the truck mounted, track supported and guided'type especially designed to use in cutting horizontal, or substantially horizontal kerfs in a minewall. A further object is to provide an improved coal mining apparatus having improved kerf cutting means, together with improved means for adjustably supporting and moving the kerf cutter. Another object is to provide an improved adjustable supporting and moving structureof the hydraulically operated and controlled type for adjusting and moving the kerf cutter in an improved manner. A further object is to'provide an improved hydraulically operated and controlled swinging and tilting means for the kerf cutter, whereby the kerf lcutter may be 'swung about its pivot and tilted about an axis extendinglongitudinally of the kerf cutter. AYet another object of the invention is to provide improved coal mining apparatus of an extremely low compact design having a novel arrangement of parts, and especially adapted to low vein work. Other objects and'advantages of the invention will, however, hereinafter more fully appear.

' In the accompanying drawings there are shown for' purposes Aof illustration one form and a modication thereof which the invention may assume in practice'.

In these drawingsi Fig. 1 is a plan view of an illustrative embodiment of the improved mining apparatus, with the kerf cutter shown in bottom cutting position.

Fig. 2 is a side elevational View of the mining apparatusshown in Fig. 1.

Fig. 3 'is an enlarged vfragmentary plan view ,K of the forward portion of the mining apparatus shown in elevation,` taken substantially on line i 1 1 of Fig. 4.

Fig. 8 is an enlarged horizontal sectional view ltaken substantially on line 8-8 of Fig. 9.

Fig. 9 is a longitudinally extending vertical sectional View taken substantially on line 9-9 of Fig. 8. f

Fig. 10 is a transverse vertical sectional view taken substantially'on line lll-I0 of Fig. 9.

Fig. 11 is an enlarged, fragmentary, transverse, vertical sectional view taken substantially on line l l-ll of Fig. '9. Fig. 12 is a view in longitudinal section taken substantially on line I2-I2 of Fig. 3. y

Fig. 13 is an enlarged transverse vertical sectional view, with parts shown in elevation, taken substantially online |3-I3 of Fig. 1.

Fig. 14 is an enlarged detail sectional view taken in the plane of Fig. 13, showing details of the'valve Icontrol means.

Fig. '15 is an enlarged detail sectional view of line l9-l9 of Fig. 9.

Fig. is a detail sectional view taken o line 20-20 of Fig. 19.

Fig. 21 is a detail sectional View taken on line 2I-2I of Fig'. 19.

Fig. 22 is a' detail sectional view taken on line 22'22 of Fig. 19.

Fig. 23 is an enlarged side elevational view, with parts shown in longitudinal vertical section, showing a portion of the clutch operating means and the hydraulic brake.

Fig. 24 is a detail view of a portion of the clutch operating means. I

Fig. 25 isa diagrammatic view showinga hydraulic fluid system and the associated control means.

Fig. 26 is a view similar to Fig. 4, of a modified form of construction showing the kerf cutter in its top cutting position.

1n lthis illustrative embodiment of the invention', there is shown a coal mining apparatus of the horizontal cutting, track cutter type, a1- though it will be evident that various features IUD thereof may be incorporated in mining apparatus of various other types, and that the apparatus may be crawler tread mounted, or mounted to slide on its bottom over the mine floor, in a well known manner. The improved coal mining apparatus disclosed herein generally comprises a self-propelled portable base, herein designated I, in the form of a truck mounted on wheels 2 adapted to travel along a trackway 3 laid on the mine floor. Supported on the truck at the forward end thereof is a horizontally swingable frame in the form of a turntable 4 overlying the front truck wheel axle, and in turn having pivotally supported thereon for swinging movement in a vertical direction with respect thereto, an elongated arm structure or boom 5 of an irnproved design, carrying at its outer extremity horizontal kerf cutting means generally designated 6. The truck I comprises a truck frame 'I of .an extremely low compact construction, and

Vthe turntable 4 is mounted in a relatively low position at the front end of the truck frame, and has a depending circular bearing portion 8 journaled for rotation about a vertical axis with respect to the truck `frame within bearing sleeves 9, 9 supported by a circular bearing support I0 formed integral with the truck frame, as shown in Figs. 12 and 13. Pivotally mounted on 'the turntable at widely spaced points, in an extreme- .ly rugged and stable'manner, is the improved arm .structure or boom 5. This arm structure or boom comprises a relatively wire, upper,jinwardly located arm or boom portion I4 mounted ina relatively low position and having spaced bearing lugs I5, I5 at each side thereof pivotally mounted on .horizontal tubular shafts I6, I6 arranged in axial alinement in `bearing lugs II secured by bracket arms I8 to the opposite sides of the turntable frame, in the manner clearly shown in Figs. 3 i and 13. Hinged at I9 on a horizontal axis parallel with the pivotal axis of the `upper arm I4, at the outer extremity of the upper arm, is an outer arm or boom portion 20, the latter having bearing lugs 2I journaled on a horizontal shaft 22 parallel with the shafts I6, I5 and supported 'within bearing supporting lugs 23 formed integral with the upper arm I4. As previously mentioned, the upper inwardly located arm I4 is widely laterally extended, as shown 'inFigs 1 and 13, and the hinged connection between the Vinwardly located upper and outer arms I4 and 2t is extremely rugged, due to its relatively wide bearing point distribution.' A pair of bottom arms 24, 24 cooperate with the'upper arm I4, and are so pivotally connectedto the turntable frame and the outer arm 2i) asto provide parallel motion means for maintaining the outer arm always horizontal and parallell toa` given straight line during swinging of the arms in a vertical direction about their pivots. Each of the lower parallel Amotion arms 24, 24 comprises a cylinder 25'having a rear head 25 formed integral with an elongated arm portion 21 pivot- Yally mounted on a pivot pin 28 arranged parallel with the horizontal shafts I6 and 22, and supported within a depending vbracket 29 integral with theturntable frame. The cylinders 25 contain reciprocable pistons 30 ofthe double- `acting type having their piston rods 3| passing through the lfront packed heads 32 of the cylinders and pivotally connected toa horizontal `shaft 33 supported within depending brackets 34 at the bottom of and integral with the outer arm 23, and likewise arranged parallel with the shafts IG and 22. The points of pivotal connection of lwithin the cutter head frame.

the arm I4 and the arms 24 with the turntable frame and their points of pivotal connection with the outer arm 2D are equally and fixedly spaced, so that when the pistons are in their midway position within the cylinders, the upper arm I4 and the lower arms 24 are parallel. When pressure fluid is supplied to one end or the other of the cylinders 25, in a manner to be later described, the pistons move in one direction or the other within the cylinders, to swing the horizontal outer arm 20 about its pivotal connection with the upper arm I4 Ieither upwardly or downwardly to change the angle in altitude of the outer arm 2i), for a purpose to be later described.

Now referring to the kerf cutting means 6, and more particularly to the driving and mounting means therefor, it will be noted that carried by the outer horizontal arm 20 is a low compact horizontal motor 35 having its casing 36 forming an intermediate portion of the arm 23, and Tthe rearmotor head 3'I is, inthis instance, formed .integral with the rear arm portion which sup- .ports -the bearing lugs 2I. The motor casing .is vprovided with a front motor head 33 having 'secured thereto, as by bolts, guide brackets 39, 33 having arcuate guideways 40 in which are guided arcuate guides 4I formed integral with .the'frame 42 of the tiltable cptter head 43,*Which .supports the kerf cutting means. The cutter `headframe is provided with a circular bearing portion 44 journaled on a bearing sleeve 45 supported by a circular bearing support 46 formed integral with the front motor head 38, and the guide lbrackets 39 retain the cuttery head frame .in position on its bearing. The means for tilt- .ing the cutter head about its vbearing on the Afront motor head will be later described. The power shaft 4l' of the motor 35 extends longitudinally ofthe outer arm 20 and has keyed to `its forward end a bevel pinion 48 meshing with a horizontal bevel gear 49, herein formed integral with a vertical shaft 50 suitably journaled Formed integral with the shaft 5I] and driven thereby, is a horizontal spur gear 5I meshing with a large spur gear 52 having its hub 53 journaled on bearings `supported by a vertical shaft 54. The spur gear 52 has its hub 53 connected to a clutch member 55, keyed to the shaft 54, by a multiple disc clutch 56 set at a predetermined load, so that when the shaft 54 is overloaded, the clutch will automatically slip to permit relative rotation between the gear and shaft. The shaft 54 is suitably journaled in bearings supported by the Vcutter head frame, and has keyed thereto, at its r'ing a circular bearing portion 6I journaled on a bearing sleeve 62 supported by a circular bearing support 63 formed integral with the cutter head frame. The cutter bar hanger frame is retained in position on its bearing on the cutter head frame by a thrust ring 64, vpreferably composed of two'semi-circular parts and secured, as Yby screws 55, to the cutter head frame, and this thrust ring cooperates with an annular ange S5 formed integral with the bar hanger frame. It will thus be seen that the cutter bar isswinga'ble horizontally relative to the cutter head about an axis coincident with the longitudinal axis of the vertical shaft 54.

the arm structure and respectively contain reci-procable single-actingpistons 1I, 1| (see Fig. '7) having their piston rods 12 extending rearwardly through the packed rear heads 13 of the cylinders. 4Secured to the rearward ends of the piston rods 12 are brackets 14 on which are journaled roller sheaves 15. A pair of cables 16 fixed at one end at 11 to the cylinder clamps 69, pass around these roller sheaves 15, and extend forwardly along the sides of the outer arm 20 and around an annular cable guiding groove 18 formed on a circular portion of the cutter bar hanger frame 6U (see Fig. 5), and the opposite ends of these cables are fixed at 19 to the bar hanger frame, in the manner clearly shown in Fig. '1. It will thus be seen that when hydraulic pressure is supplied to the forward end of one of the cylinders and is exhausted from the forward end of the other cylinder, one of the cables may be deected rearwardly, while the other cable is slackened, to eect swinging of the cutter bar hanger frame o-n its bearing on the cutter head frame, and as a result, the cutter bar may be swung horizontally in one direction or the other about its pivot. By trapping the liquid in the cylinders the cutter bar may be locked against swinging movement about its pivot relative to the arm structure.

The means for rocking the kerf cutter carrying cutter head 43 on its bearing to tilt the 4,0 cutter bar about a longitudinal axis relative to the outer arm comprises, as shown most clearly in Fig. 6, a pair of vertical cylinders 8|, 8| secured to the arm and preferably formed integral with the guide brackets 39 and contain- 45 ing piston-like plungers 82. These plungers extend downwardly from the cylinders and engage lateral shelf-like lugs 83 formed integral with the cutter head frame at its opposite sides. It will be evident that when hydraulic pressure is supplied to the upper end of one or the other to the outer arm 20. By trapping the liquid within the cylinders the cutter head may be locked against tilting movement relative to the arm structure. The means for supplying hydraulic pressure to the cylinders 68 and 8| will be hereinafter described.

Now referring to the means for swinging the arm structure or boom 5 in a vertical direction relative to the swiveled turntable frame 4, it will be noted that pivotally mounted on a horizontal shaft (see Fig. 4) supported by the bracket 29 in parallelism with the shaft 28 and below the latter, is a relatively large, centrally located, hydraulic cylinder 86 containing a reciprocable double-acting piston 81 having its piston rod 88 extending forwardly and upwardly through the front packed head 89 of the cylinder. The forward end of the piston rod 88 is pivotally connected to the horizontal shaft 22 at a point midway between the lower parallel arms 24, 24, the upper arm I4 being cut away at 90 to provide clearance for the cylinder head as the arm structure is swung in a vertical direction about its pivotal mounting. It will thus be seen that when hydraulic pressure is supplied, in a manner to be later explained, to one end or the other of cylinder 86 the arm structure may be swung either upwardly or downwardly, and by trapping the liquid within the cylinder 86 the arm structure may belocked in its adjusted position. It will further be evident that when the arm structure is swung either upwardly or downwardly about its pivot and the pistons of the lower parallel arms 24 are in their mid-way positions, shown in Fig. 12, the outer arm 29, together with the kerf cutter supported thereby, will always be maintained horizontal.

The mechanism for rotating the swiveled turntable frame 4 about its axis to .swing the cutter supporting arm structure horizontally relative to the truck comprises a pair of hydraulic cylinders 92 arranged in longitudinal parallel relation at the opposite sides of the truck frame and having their rear ends pivotally mounted on vertical pivot pins 93 supported within lugs integral with the truck frame, so that the cylinders are permitted to swing horizontally. `Reciprocable within these cylinders are double-act,- ing pistons 94 having their piston rods 95 extending'forwardly through the front packed cylinder heads 96 and pivotally connected at their forward extremities by vertical pivot pins 91 to lugs 98 integral with the bearing lugs I1. It will be evident that when hydraulic pressure is supplied, in a manner to be later described, to

one end of one cylinder and to the opposite end of the other cylinder, the pistons may bemoved in relatively opposite directions to effect turntable rotation. By trapping the liquid in the cylinders, the turntable frame may be locked against rotation.

Now referring to the improved propelling means for the apparatus, it will be noted that supported on the rearward portion of the truck frame at a substantial distance rearwardly of the swiveled turntable frame for the arm structure, is a horizontal motor 99 having its power shaft |89 horizontally disposed and extending longitudinally of the apparatus. As shown in Fig. 8, splined at ||l| to the forward end of the motor power shaft is a sleeve-like hub |82 of a spur motor pinion |83. The hub of the spur motor pinion is suitably journaled within bearings supported within the frame of a transmission gear housing ||l4 supported on the ,truck frame in advance of the motor, and the motor pinion meshes with a spur gear |65 keyed to the rear end of a horizontal transmission shaft |06. The transmission shaft |96 is herein arranged in parallelism with the motor power shaft, and likewise suitably journaled within the transmission gear housing |04, Secured to and driven by the shaft |96 is a spur gear |91 meshing with a large spur gear |98 having its hub journaled on bearings supported on a horizontal transmission shaft |99. The shaft |09 is arranged in parallelism with the transmission shaft |96 below the latter, and is likewise suitably jo-urnaled within the transmission housing. Also fixed to and driven by the transmission shaft |06 is a worm |||l meshing with a horizontal worm wheel II| (see also Figs. l0 and l1), keyed to the upper end of a vertical shaft H2. The shaft I2 is suitably journaled within the transmission housing and has fixed thereto and drives a worm I I3 meshing with a worm wheel 4 arranged coaxially with the spur lgear |66 andlikewise having its hub journaled 'on `bearings supported by the transmission shaft |69. The spur gear |08 herein lconstitutes the high speed terminal driving element of the high speed transmission, while the Worm wheel ||4 constitutes the low speed terminal driving element of the low speed transmission, and these gears |68 and |I4 are connectible by multiple disc clutches I5 and I I6, respectively, to the shaft |69. It will thus be seen that when one or the other of the clutches H5, I |6is applied, the shaft |89 may be driven either at a relatively low speed or at a relatively high speed. As shown in Fig. 8, keyed to the forward end of the transmission shaft |69 is a bevel gear H1 meshing with reverse bevels H8 and ||9 and driving the latter in relatively opposite directions. The hubs of these bevel gears H8 and I |9 are journals-d on bearings supported by clutch members |26 keyed to a horizontal transmission shaft |2I, and the reverse bevels are alternately connectible in driving relation with the shaft |2| by multiple disc clutches |22 and |23, respectively, so that the shaft may be driven in one direction or the other. The shaft |2| extends transversely of the transmission housing and is suitably journaled in bearings supported therein, and has keyed thereto, at its opposite ends, chain sprockets |24, |24 connected by endless drive chains |25 to chain sprockets |26, |26 keyed to rear stub axles |21, |21, respectively. These stub axles also have keyed thereto chain sprockets |28 which ,are connected by endless `drive chains |29 to chain sprockets |30, keyed to the front axle |3I. The rear stub axles |21 and. the front axle 13| have fixed thereto and drive the truck wheels 2. From the foregoing it will be evident that through the transmission gearing above described, the truck wheels may be driven at either a relatively low speed or .a relatively high speed and in either of opposite directions at either speed.

The operating means for the high and low speed disc clutches ||,5, 6 comprises a clutch shipper ring |33 surrounding the shaft |69 between the high and low speed terminal gears |68 and I i4, as shown in Fig. 8, and this ring is journaled on ball bearings supported by a sleeve |34 in turn slidably mounted on a cylindrical member |35 supported by the shaft, and this clutch shipper ring has projections engaging the adjacent end discs of the clutches, so that when the shipper ring is moved in one direction or the other, one of the clutches is applied, while the other is released. Engaging the clutch shipper ring is a shipper yoke |36 secured to an operating shaft |31 rotatably mounted at its opposite ends within the side Walls of the transmission housing, and keyed to one end of this operating shaft is an upstanding lever |33 pivotally connected at its upper end at |39 to a swingable frame |46. This frame has a guideway 4| in which is slidably mounted a block |42 having a socket |43 for receiving an eccentric |44 formed integral with a spur gear |45. This spur gear is fixed to a horizontal shaft |46 extending transversely of and suitably journaled within the transmission housing. Fixed to the other end of the horizontal shaft |46 is a similar spur gear |41, and meshing with these spur gears are spur gears |43 and |49 fixed to operating shafts |56 and I5| herein arranged in alinement on horizontal axes extending transversely of and suitably journaled within the opposite sides of the gear housing. Fixed to the outer ends of the operating shafts |51) and |5| are operating handles |52 convenientlylocated at the opposite sides of the apparatus. It will thus be seen that when the operator grasps one of the handles and rotates the gears, the shipper yoke lever |38 is swung about its pivot to move the shipper ring in one direction or the other to apply one or the other of the disc clutches. The operating means for the reverse bevel clutches |22, |23 comprises a similar clutch shipper ring |54 with which engages a pivoted shipper yoke |55 having an integral operating lever |56. Mounted within the transmission housing are alined horizontal cylinders |51, |51 containing pistons |58, |58 having plunger-like piston rods engaging the opposite sides of the outer end of the shipper yoke lever |56. Acting on the pistons are coil springs |59 for constantly urging the plungers into engagement with the shipper yoke lever for normally maintaining the clutch shipper ring in its neutral position. When hydraulic pressure is supplied, in a manner to be later explained, to one or the other of the cylinders |51, one of the pistons |58 may be moved to swing the clutch shipper yoke about its pivot, thereby to move the clutch shipper ring in one direction or the other to apply one of the reverse clutches.

The journal structure for the stub axles |21 is clearly shown in Fig. 10 and comprises spaced vertical inner and outer frame portions |6| formed integral with the truck frame and connected by an upper horizontal integral frame portion |62, and the vertical frame portions support alined bearing sleeves |63 in which the stub axles |21 are journaled. In this instance, the chain sprockets |26 are arranged at the inner adjacent sides of the inner vertical frame portions |6I, while the truck wheels and the chain sprockets |28 are secured to the stub axles between the vertical frame portions |6I. By rearranging the position of the wheels and sprockets with respect to the stub axles, the track gauge may, of course, be varied.

A hydraulic jack is provided for jacking the apparatus in position on the mine trackway during the cutting operation, and this jack is arranged coaxially with the swiveled turntable frame 4 andis supported thereby. As shown in Fig. 13, this jack comprisesa vertical cylinder |65 containing a double-acting piston |66 having its piston rod |61 projecting upwardly through the packed upper head |68 Aof the cylinder. The lower cylinder head |69 is seated within a bore formed within the circular bearing portion 8 of the swiveled turntable frame, and the upper head is arranged in an alined bore, and the cylinder heads are secured in position by screws |10 engaging lugs integral with the upper head and threadedly secured within the turntable frame. The upper extremity o-f the piston rod is formed with a point |1I adapted for vreceptionwithin a socket vformed within a conventional mine roof jack, and when it is desired to jack the apparatus in position on the trackway, hydraulic pressure may be supplied, in a manner to be later described, to the lower end of the cylinder to effect upward movement of the piston, thereby causing rigid engagement of the mine roof jack with the mine roof. When hydraulic pressure is supplied to the upper end of the cylinder, the jack is, of course, released. For braking the truck wheels there is provided a truck wheel brake |12 comprising a brake drum |13 lxed to one of the rear stub axles I 21, and with which is engageable a contractible brake band |14. This brake band is operated through usual lever and link mechanism |15 by a hydraulic brake release cylinder |16. The cylinder houses a coiled spring (see Fig. 8) for always urging the brake operating means toward brake applying position.

Mounted for rotation about a vertical axis on the rearward portion of the truck frame rearwardly of the truck driving motor 99 is a horizontal reel |11 for the motive power conducting element for the motors 35 and 99, and this power conductor reel is adapted to be driven through the high and low speed transmission gearings above described, by a bevel gear |18 secured to the transmission shaft |09 (see Fig. 8). As shown in Fig. 9, the bevel gear |18 mesheswith a bevel gear |19 secured to a vertical shaft |80 suitablyjournaled within the transmission housing. Keyed to the lower end of the vertical shaft |80 and driven thereby is a chain sprocket |8| connected by an endless drive chain |82 to a chain sprocket |83 fixed to the reel drive shaft. 'I'he reel drive shaft may be frictionally connected in.

apparatus is propelled rearwardly along the ,mine

trackway at either a high or a low speed, the-reel |11 will be simultaneously driven at a similar :speed to wind in the power conductor element under the control of the high and low speed disc clutches and V|||i. When the apparatusis propelled forwardly along the trackway, the friction reel drive slips to pay out the power conductor element. l

Now referring tothe improved hydraulic fluid system and the associated control means for sup-v plying liquid under pressure to the various hydraulically operated devices, it will be observed that formed in the gear housing |04 is a chamber |90 (see Fig. 8) providing a reservoir for containterminal gear |08 of the high speed transmission.`

As shown in Figs. 1 and 13, supported on the top 4of the swivelled turntable frame 4 is a front valve box |95 containing valves for controlling thebar swinging cylinders y68, the cutter head tilting cylinders 8|, the parallel arm cylinders 25, the

cylinder 86 for vertically swinging the arm structure, and the jack cylinder' |65, while supported on the top of the gear housing is a rear valve box |96 containing valves for controlling the supply of hydraulic pressure to the brake vcylinder |16, the cylinders |51 for controlling the reverse bevel clutches and the cylinders 92 for horizontally swinging the arm structure.' Fig. 17, the front valve box |95 has formed therein a series of parallel horizontal bores having reciprocably mounted therein slide valves 91, |98, |99 and 200 and a rotary valve 20|, while, as shown inFig. 19, the valve box |96 has formed therein parallel horizontal bores containing slide valvesY 202 and 203. As shown in Fig. 25, the pump; |9| has its pressure side connected through a conduit 204 to a liquid pressure supply passage 205 in the valve box |96 Vand a liquid pressure supply passage 206 in thev valve box |95, while the discharge side of the pump is connected through a conduit 201 to the discharge passage 208 of the valvexbox |96, 4and the discharge passage209v As shown in of the valve box |95. Formed inthe valve box |95 and extending in parallel relation substantiallyfthereacross are supply and discharge passages 2|0 and 2|| communicating respectively with the passages 206 and 209, and these passages 2|0l and 2|| communicate with all of the Valve bores. with thebores containing the slide valves midway between the endsv thereof and with one end of the bore containing the rotary valve 20|, while the discharge passage 2|| communicates with the valve bores at the left hand ends thereof, asy

viewed in Fig. 17, and is connected through passages 2|2 and 2|3 with discharge passages 2|4 communicating lwith the right hand ends of the bores for the slidel valves, as viewed in Fig. 17; The slidevalves are` herein of the balanced spool type comprising'spaced end spools 2|5, 2|5 con- The supply passage 2|0 communicatesnected by a reduced portion 2|6, and the supply passage 2|0 communicates with the annular spaces encircling the reduced portions between the end spools, while` the exhaust passages communicate ywith the valve bores at the remote ends` Communicating with the of the valve spools. borefcontaining the slide Valve |91 are ports 2|1 and 2 |8 (Fig. 17) respectively connected by con- -duits 2 9 and 220 (Fig. 25) with the opposite endsv of the cylinders 25 of the lowerparallel arms 24.

Communicating with the bore containing the slide valve |98 are ,ports 22| and 222 (Fig. 17) respectively connected by conduits 223 and 224 (Fig. 25) to the opposite ends of the .cylinder 86 for vertically swingingthe arm structure. Communicating with the Vbore containing the slide valve |99 are .ports 225 and 226 (Fig. 17) respectivelyy connected by. conduits 221 and 228 (Fig. 25) to the upper ends of the cylinders 8| for rocking the cutter head frame about the longitudinal axis of the outer. arm. Communicating with the bore containing the slide valve 200 are ports 229 andv 230 (Figs. 17 and 18), respectively connected by conduits 23| and 232 (Fig. 25)v to the forward ends of the bar swinging cylinders 68. The bore containing the rotary valve has communicatingtherewith, respectively at the top and bottom thereof, ports 233 and 234, respectively connected'f by conduits 235 and 236 (Fig. to the opposite ends of the jack cylinder |65, and the rotary valve has longitudinal grooves 231 and 238 opening out' through the opposite ends thereof respectively, for connecting the ports 233 and 234 with either the supply passage or the exhaust passage.

In the rear valve box |96, the liquid pressure supply passage 205 communicateswith a supply' passage 239 (Figs. 19 and 21) in turn communieating with the bore containing the slidev valve 202 midway between the ends thereof, while the o discharge passage 208 communicates with discharge passages 240 and 24| (Fig. 19) in turn communicating with the bores containing the slide valves 202 and 203 at the remote ends thereof. The slide valve 202.is similar to theslide valves above described, and similarly has spaced end spools 242 and 243 connected by a reduced portion` 244, and the supply passage 239 communicates with the annular space surrounding the reduced portion between the spools. 'Ihe supply passage 239 is communicable with the discharge passage; 208; under the control of a bypass valve 245('seeFig. 19) operable by a pivoted lever. 246` extending Aacross .the top of the truck 1 cating with the valve bore.

:end of the other.

pass valve 245 may be opened to connect the supply conduit 284 with the discharge conduit 281 to relieve the pressure in the supply passages in bothv valve boxes, so that the liquid pressure in the system may be reduced at will. The slide valve 283 is herein of the three-spool type having end spools 248, 248 (Fig. 19) and a` central spool 249 connected by reduced portions, and an axial passage 250 in the valve is connected at its ends by radial ports 25| with the discharge passages 248, 24| respectively, at the ends of the valve bore, and radial ports 252 communicate with an annular groove 253 formed centrally on the periphery of the central valve spool 249 and communi- Communicating with the bore containing the slide valve 282 are ports 254 and 255 (Fig. 19) communicating, respectively, with passages 256 and 251 connected by conduits 258 and'259, respectively, (Fig. 25) with the cylinders 92 forhorizontally swinging the arm structure, the conduit 258 being connected to one end of one cylinder and the opposite kend of the other, and the conduit'259 connected to the opposite end of the first cylinder and the opposite Communicating with the bore containing the slide valve 263 are ports 260 and 26| (Fig. 19) connected by conduits 262 and 263 (Fig. 25) to the outer ends of the cylinders |51 for controlling the reverse bevel clutches, and communicating with the valve bore, midway between the ports 260 and 26|, is a port 264 connected by a conduit 265 to the brake cylinder |16. The supply passage 239 in the rear valve box |96 is connected through a port 266 controlled` by a ballcheck valve 261 (see Fig. 21) with a passage 268 in turn communicating with a transverse passage 269 (Fig. 20) connected through ports 219 and 21| with the annular spacesy surrounding the reduced portions of the valve 283 between the valve spools. The ball check valve permits ow of liquid pressure from the'supply passage 289 to the passage 268, while liquid ow in the reverse direction is automatically prevented thereby. In Figs. 1'1 and 19, all

, of the slide valves and the rotary valveare shown in their closed or neutral position, so that the liquid pressure in the supply passages may flow past the by-pass valve 245 throughY the discharge passages back to the pump intake or reservoir. When the slide valves in the front control box |95 are slid in one direction or the other, certain of the ports may be connected to the liquid pressure supply, while the other ports are connected to the discharge passage, so that the various hydraulic devices controlled thereby may be operated in one direction or the other, and when the valves are in the neutral position shown, the liquid is trapped within the hydraulic devices controlledr thereby. The ports communicating With the bore containing the rotary valve` 28|, upon rotation of the valve in one direction or the other, may be connected either with the pressure supply passage or with the discharge passage, so that the hydraulic jack may be moved either upwardly or downwardly, as desired, and when the valve is in the position shown, the liquid is trapped Within the cylinder to, lock the jack in position. When the slide valve 202 in the rear valve box |95 is slid in one direction or the other, one or the other of the ports is connected with the supply passage, while the other port is connected with the discharge passage, thereby to effect movement of the pistons of the hydraulic swinging cylinders 92 for the armstructure in one `direction or the other toswing the arm. structure horizontally. in either of opposite directions. When the slide; valve 203' in the rearA valverbox |96 is in the position.shownthe.reverse bevel clutch-operating cylinders |51 and the brake cylinder |16 are connected to"y the discharge passage, and when' the slide valve is slid in one direction or the1otherliquid under pressure is supplied to one or the other of the reverse' bevel clutch operating cylinders and tothe brake cylinder to effect application of. one or the other of thelclutchesand to release theV brake. VWhen one reverse bevel clutch is applied, they brake is always .maintained released.

Now referring to the improved operating means for theslide` valves |91, |98, |99, and 298, in the front valve box |95, it will be noted that each valvev has a valve stem. 215 (Fig. 1'1) projecting outwardly from thevalve box through a sealing packing 216, and secured to the outer end of each valve stem is a grooved member 211, andengaged in the grooves in these members are shipper yokes 218, 219, 286 and 28|, respectively (Fig. 13). The shipper yoke 218 for the slide valve 288 is keyed to a tubular operating shaft 282 (Fig. 14) rotatably mounted in the bore of and extending centrally through one of the tubular shafts i6 on which the arm structure is pivotally mounted. Rotatably mounted in and extending centrally through the bore of the .other tubular shaft I6 at the opposite side of the ap paratus, is a-tubular operating shaft 283 alined with the sha-ft 282 and having keyed thereto a connecting member 284, of semi-circular cross section (Fig. 16), keyed at its opposite end to the shaft 282, and the remote ends of the tubular shafts 282 and 283 have xed thereto operating leversv 285 conveniently'located at the opposite sides of the apparatus in adjacency with the control handles 241 and |52 for the by-pass valve and the speed control clutches of the transmission. The shipper yoke lever 2'19 for the valve |99 is keyed to a tubular operating shaft 286 rotatably mounted in and extending centrally through the tubular shaft 282, and this shaft 286 has keyed thereto a connecting member 281 likewise of semi-circular cross section (Fig.` 16) and extendingv transversely within the member 284 and keyed at its opposite endv to a tubular operatingA shaft 288, alined with the shaft 286 and extendingv centrally through and rotatably mountedv in thev bore of the tubular shaft 283, and the remote ends of the' operating shafts 286 and 288 have fixed thereto operating levers 289 located in adjacency to theoperating levers 285. The shipper yoke lever 288 for the slide valve |98`is keyed to a tubular operating shaft 290 extending centrally through andv rotatably mounted in thetubular shaft 286 and keyed to a connectingr member 29|, in turn keyed to a tubular operating shaft `292 extendingV centrally through and rotatably mounted in the tubular operating shaft 288, and these operating shafts 290 and 292 have fixed thereto at their remote ends; in adjacency to the levers 285 and 289,' operatinglevers 293. The shipper yokelever28| for the slide valve |91 isV keyed to an operating shaft 294 extending centrally through'. and: rotatably mounted in the tubular operating.. shafts 290 and 2.92 and have fixed thereto, at its remote ends in. adjacency to the other levers, operating levers-295. Eachpof the operating` levers has a spring-pressed locking plunger. 296 engageable with..notches inl the outer face off a-A side plate291 'secured to, 'at 298', and supported by thebearing shaftsl for'the arm vstructure and having projecting lugs 299 interlocked at 300 with notches in the adjacent sides of the swiveled turntable frame, so that the slide valves may be locked in their different operative positions. Fixed to the plates 291 and projecting outwardly over the operating levers, are shields'30l for protecting the levers. The rotary control valve 20| for the hydraulic roof jack has a valve stem 302 (Fig. 17) projecting -outwardly through a sealing packing 303 and having a manual operating lever 304. As shown in Fig. 19, the slide valve 202 has valve stems 305 projecting outwardly from the rearvalve box |96 through sealing' packings 306, and secured to these .valve stems are valve operating rods 301 having grasping portions conveniently located at the opposite sides of the apparatus in `adjacency to the con-'- trol levers above described. Threadedly secured `;within the opposite ends of the slide valve 203 (Fig. 19) are valve stems 308 projecting outiwardly from the valve box through sealing packings 309 and having operating rods 3|0 (Fig. 1) provided with grasping portions located at the opposite side of the machine in adjacency to the grasping portions for the operating rods 301. Encircling the valve stems and interposed between the operating rods in the outer sides of the valve box are oppositely acting coil springs 3|| forv maintaining the slide valve 203 in its midway neutral position.

In the modified form of construction shown in Fig. 26, the Ycutter head is inverted, with respect to the outer arm or boom portion 20, with the kerf cutter in its! top cutting position instead .of in the bottom .cutting position shown in Figs. 4 and 5. In this construction, the bolts securing the cutter head frame to the front motor head 38 are detached and the head turned through on its bearing 44, 45 and 46 on the motor head 38, and the holding bolts thereafter reinserted and tightened to hold rigidly the cutter head in position on the outer end of the arm. n this modiiied form of construction, the arm structure may be operated to adjust the kericutter in a horizontal cutting position at the roof level and through a series of parallel hori- Zontal cutting planes between the roof level position and a horizontal 'cutting position spaced a substantial distance below the roof level, while.

'in the embodiment of the invention above described, the kerf cutter operates to cut through a series of lower horizontal cutting planes including a horizontal cutting position at the floor` level. The cutter head is, of course, tiltable with respect to the arm about the longitudinal axis of the arm by means of the hydraulic tilting cylinders 8|. lOtherwise, this form of the invention is identical to that above described. It will thus be evident that instead of detaching fthe head and inverting the same, the cutter head ,may be mounted on the outer extremity of the horizontal outer arm for rotation within its bearing so as to make a complete revolution about its axis relative to the arm, and, if desired, power operated means of the type well known to those skilled in the art, may be provided for effecting complete head rotation. v

The general mode of operation of the improved coal mining apparatus will be clearly apparent from the' description given. The apparatus may be propelled along the mine trackway from one working place to another by the truck propelling mechanism under the control of the high speed friction clutch l5 of the high speed transmission mechanism driven by the motor 99, or at a relatively low speed under the control of the friction clutch |I6 of the low speed transmission mechanism, and the apparatus may be propelled along thetrackway in either of opposite directions at either speed under the control of the reverse bevel friction clutches |22 and |23. When the working place is reached and it is desired to cut a horizontal kerf at the level of the mine floor outside and below the level of the mine track-` way in accordance with the arcwall method of cutting, the operator operates the slide valve 202 to supply hydraulic pressure from the pump I9I to the swinging cylinders 92 to effect swinging of the arm structure 5 horizontally about the turntable axis relative to the truck from the centrally locatedy transport position shown in Fig. 1 to a position wherein the cutter bar 59 is located at the right-hand side of the trackway with its pivot lying outside the trackway. As the arm structure 5 is swung horizontally about the turntable axisl relative to the truck frame, hydraulic pressure may be supplied to one of the bar swinging cylinders 68, under the control of the slide valve 200, to effect swinging of the cutter bar 59 about its pivot in the opposite direction until the tip end of the cutter bar assumes a position at the right handrib. Hydraulic pressure may then be supplied to the cylinder 85, for vertically downwardly swinging the arm structure, to move the cutter bar into a horizontal cutting position at the level of the mine floor outside of the trackway, under the control of the slide valve |98.

When the cutter bar is in a position to cut a horizontal kerf at the level of the mine floor outside and below the level of the mine trackway, the operator applies the low speed clutch ||6 and the forward feed reverse bevel clutch |9 of the truck propelling mechanism, and the apparatus may be propelled bodily along the mine trackway to effect sumping of the cutter bar beneath the coal seam. Upon completion of the sumping cut, the low speed clutch IIB is released and the slide valve 203 moved into a position to effect release of the reverse bevel clutch and to effect application of the truck wheel brake. may then be engaged with the hydraulic jack piston on the apparatus, and the rotary valve 20| may then be operated to supply hydraulic pressure to the lower end of the jack piston rigidly to jack the apparatus in stationary position on the mine trackway. The operator then moves the slide valve 202 into a position to supply hydraulic pressure to the cylinders 92 for horizontally vswinging the arm structure about the turntable axis, thereby eiecting swinging of the kerf cutter from its position at the right hand rib transversely across the coal face into a position wherein the tip end of the cutter bar is in adjacency to the left hand rib. During horizontal swinging of the cutter bar from right to left, the operator may move the slide valve 200 into a position to supply hydraulic pressure to one of the bar swinging cylinders 68 to effect swinging of the cutter bar about its pivot in the opposite direction to first straighten up the bar and thereafter to move the bar into an opposite angular relation, so that upon completion of the transverse swinging cut the cutter bar vis located at the left hand rib with its tip end at the left hand rib and itspivot located outside and below the level of the trackway. The valves 200 and 202 are then moved into their neutral position, and the valve 203 is moved into a position to apply the reverse feedlbevel clutch and to eiect release of the brake, and

A mine roof jack upon application of the low speed transmission clutch i i6, the apparatus is propelled bodily rear wardly along .the mine trackway to effect withdrawal of the cutter bar from beneath the coal face. Upon proper adjustment of the valves |98, 200 and 202, the arm structure and cutter bar are then returned to their transport position indicated in full lines in Fig. 2. Duringr the horizontal cutting operation if it is desired to tilt the cutter bar to change its angle in altitude and to rock the cutter bar edgewise about the longitudinal axis of. the outer arm 2i), this may be accomplished by supplying hydraulic pressure to the cylinders 25 of the lower parallel arms 24 to change the length of the latter and move the arms 24 and i4 out of parallelism, thereby to tilt the outer arm 2i) and cutter bar either upwardly or downwardly about the axis oi the pivotal connection between the outer arm 2b and the upper arm I4, and by supplying hydraulic pressure to one or the other of the rocking cylinders 8l, to tilt edgewise the cutter bar about the longitudinal axis of the outer arm 2i). If it is desired to cut horizontal kerfs in the coal seam at different elevations with respect to the mine floor, hydraulic pressure may be supplied to the cylinder 86 to swing the arm structure 5 upwardly about its pivotal connection with the turntable, and in any elevated position of the cutter bar, the latter may be sumped in, swung transversely in its plane across the coal face and withdrawn from the coal face in the manner clearly described above. During adjustment of the kerf cutter into different horizontal cutting positions in horizontal planes at dierent elevations, the parallel motion arm structure, intervening the turntable and outer arm 2G, acts automatically to maintain the arm 20 and cutter bar in a horizontal position, regardless of thel angular position of the arm structure about its pivotal connection with the turntable frame. By rocking the. cutter bar about its transverse and longitudinal axes relative to the parallel motion arm structure during the cutting operation, it is possible to move the cutter bar to accommodate itself to a rolling bottom or pitching coal seam. When the cutter head frame is inverted with respect to the outer arm 2l), as disclosed in the modication shown in Fig. 25, the cutter bar may be operated to cut a horizontal kerf at the level of the mine roof or in horizontal cutting planes at different elevations with respect to the mine roof, and, as in the form of the invention above described, the

,cutter bar may be rocked about transverse and 55 o. type known as a track cutter is provided, wherein u horizontal kerfs may be cut in a mine wall at variousY elevations in an improved manner. It will further be noted that by theprovision of the adjustable supporting structure for the kerf cutter, a horizontal cutting apparatus is attained having relatively great universality. It will still further be evident that by the provision of the improved swinging and tilting mechanism for the kerf cutter, it is possible to move the kerf cutter into different cutting positions in an improved manner. It will also be noted that by the provision of rthe hydraulic adjusting means for the swinging'and tilting mechanisms for the kerf cutter, it is possible to move the Vkerf cutter at any desired speed under perfect control and to maintain the kerf cutter in its. adjusted position. Other uses and advantages of the improved coal mining apparatus Will be clearly apparent to those skilled in the art.

While there are in this application specifically described one form and a modification thereof which the` invention may assume in practice, it will be understood that this form and modication of thesame are shown for purposes of illustration and that the invention may be further modified and embodied in various other forms without departing from its spirit or the scope of the appended claim.

What I claim as new and desire to secure by Letters PatentY is:

In a mining apparatus, in combination, a sup- 9 port, a second support mounted on said rst support to rock relative thereto about an axis extending longitudinally of said first support, a kerf cutter pivotally mounted on said second support to swing horizontally relative thereto about a vertical axis perpendicular to the plane of the kerf cut thereby, means for swinging said kerf cutter in .either of opposite directions about its pivot comprisingy a pair of parallel cylinders mounted on said latter support and extending longitudinally along the opposite sides of said first support, the forward ends of said cylinders extending forwardly in advance of a transverse verticalplane including the korf cutter pivot axis, pistons reciprocable in said cylinders and operatively connected to said kerf cutter, and means for supplying fluid under pressure selectively to said cylindersto actuate one or the other of said pistons, and means for rocking said second support in either of opposite directions relative to said rst support comprising a pair of parallel cylinders mounted on said iirst support and arranged in a vertical position at the opposite sides of said second support at the inner sides of said rst mentioned cylinders, pistons contained in said vertical cylinders and engaging said second support, and means for supplying uid under pressure selectively to said vertical cylinders.

JOSEPH F. JOY. 

